Pilot-controlled distributing valve for fluid-operated motors



c. J. coBERLY 2,580,657

6 Sheets-Sheet l Jan. 1, 1952 PILOT-CONTROLLED DISTRIBUTING VALVEAFOR FLUID-OPERATED MOTORS Filed March 18, 1946 Jan. 1, 1952 c. J. Coal-:RLY

PILOT-CONTROLLED DISTRIBUTING VALVE FOR FLUID-OPERATED MOTORS Filed March 18, 1946 6 Sheets-Sheet 2 l? THE F/RM A TTG/QN: ys

C. J. COBERLY' Jan. 1, 1952 PILCT-CONTROLLED DISTRIBUTING VALVE -FOR FLUID-OPERATED MOTORS 6 Sheets-.Sheet 3 Filed March 18, 1946 ZN VEN To@ am EH B oa. .O on C5 .T d@ @F H, MK, 5f

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A Tram/Em- 6 Sheets-Sheet 4 C. J. COBERLY Jan. 1, 1952 n PILOT-CONTROLLED DISTRIBUTING VALVE FOR FLUID-OPERATED MOTORS Filed March 18, 1946 Jan l, 1952 c. J. coBERLY 2,580,657

PILOT-CONTROLLED DISTRIBUTING VALVE FOR FLUID-OPERATED MOTORS Filed March 18, 1946 6 Sheets-Sheet 5 n FOR 7HE FIRM ,4 Troma/s Patented `Ian. 1, 1952 PILOT-CONTROLLED DISTRIBUTING VALVE FOR FLUID-,OPERATED MOTORS Clarence J. Coberly, Los Angeles, Calif., assignor, by mesne assignments, to Dresser Equipment Company, Cleveland, Ohio, a corporation of Ohio Application March 18, 1946, Serial N o. 655,329

17 Claims.

My invention relates to a :duid-operated motor and. more particularly, to such a device having a reciprocating motor piston in which the velocity of the motor piston `is automatically controlled whenthe working load on such piston is reduced below a predetermined Value.

This invention is an improvement on the device disclosed in my earlier Patent No. 2,311,157, issued February 16, 1943. to which reference is hereby made for a detailed discussion of the problem in the art.

Although my' invention is of particular utility in the oil industry in combination with a pump for pumping oil from a well, and for the purpose of illustration is described in connection with such use, it will be apparent to those skilled in the art that it is susceptible of other and diiierent uses, and, consequently, I do not intend to be limited to the particular use described.

In general, in the oil industry it is common practice to use a fluid-operated pump in pumping oil from a well, such a pump generally comprising a coupled motor and pump combination set in the well at the level from which it is desired to pump the oil. In such a pumping device, the motor is normally actuated by admitting operating fluid, such as oil, under relatively high pressure alternately to opposite ends of a motor piston to reciprocate the same, the reciprocation of the motor piston being suitably communicated to a pump piston in the pump end of the device so as to pump oil from the well. In order to conduct operating fluid alternately to opposite ends of the motor piston, a mainy valve mechanism isv ordinarily employed, such as is shown, vin my" said Patent No. 2,311,157, and the present inven-l tion has the same objects specied in saidpatent and additional objects as will appear hereinafter. l

The governing valve construction disclosed inV said Patent No. 2,311,157, as pointed out therein, is adapted to prevent the motor and pump pistons of a fluid-operated pump from racing at exces-` sivev speeds when the pump working load dropsY below a predetermined percentage of its normal operating value. described in said patent, with such a reduction in pump load, the pistons could speed up somewhat, as illustrated in Fig. 22 thereof, to a-connormal pumping. With the prior device-the increase in speed permitted was as high as 50% greater than the normal 'piston speed; and I have 7 found lthat even such a controlled increase inf well pumping installations. Consequently, it is a primary object of this invention to provide av governing valve for such a pump which, upon any reduction in pump working load, will main' tain the piston speed at or below its normal operating speed during the period in which the pump load is reduced. I have found it to be very desirable to reduce substantially the piston speed during such period, e. g., to only one-half its normal speed, and this is a further object of my invention.

The valve construction disclosed in my prior some well installations.

" connecting the interior of. the valve mechanism However, in the embodiment.

with the space surrounding the pump through which the production flow from the well passes upwardly to the surface of the ground from the pump. Where the pump-is installed in a well in which substantial amounts of sand are carried. upwardly with the production Aiiow, such sand. sometimes enters the valve port and damages It is therefore anotherv the valve mechanism. object of the present invention to provide, instead of such a direct port, a relatively long and tortuous passage serving the same purpose so far asl the valve mechanism is concerned, but which, by

reason of its length and character, inhibits theL entry of sand into the valve mechanism.

Another disadvantage of the valve mechanismv shown in my Patent No. 2,311,157 is that it can,

under some conditions of operation, occasionally stop on dead center so as to stop operation, which is undesirable. It is another object of the present invention to provide a valve of this type in which. the passages and ports are so arranged that it 1 cannot in any event stop on dead center during operation.

Other objects and advantages will be eviden from the following specification and the drawings, which are for the purpose of illustration;

only and in which:

Fig. 1 is a vertical sectional view of the motor= and main valve of my invention;

Fig. 2 is a vertical sectional view of my invenl tion, carried downwardly from the lower end of Fis. 1;

l y Fig. 3 is a vertical sectional view of my inventrolled but higher rate of speed than utilized in tion, carried downwardly from the lower end of,

JFig. 2;

Fig. 4 is a cross-sectional view taken on the line 4-4 of Fig. 1;

Fig. 5 is a cross-sectional view taken on the line piston speed'may b e excessivein certain d eeplv 5--5 of Fig.1;

Fig. 6 is a cross-sectional view taken on the line 6-6 of Fig. 1;

Fig. 'l is a cross-sectional view taken on the line l-l of Fig. l;

Fig. 8 is a cross-sectional view taken on the line 8-8 of Fig. 1;

Fig. 9 is a cross-sectional view taken on the line 9-9 of Fig. l;

Fig. 10 is a cross-sectional View taken on the line Ill-I6 of Fig. l;

Fig. 11 is a cross-sectional view taken on the line ofFig.1;

Fig. 12 is a cross-sectional line |2|2 of Fig. 1;

Fig. 13 is a view showing the outer surface of the main valve of my invention projected onto a vertical plane;

Fig. 14 is a vertical sectional view of my invention, showing the main valve in one position of operation;

Fig. 15 is a vertical sectional view of my invention, Showing the main valve in another 4position of operation; y

Fig. 16 isa vertical sectional view of my invention, showing the main valve -in another position of operation;

Fig. 17 is a vertical sectional View of my invention, showing the main valve in another position of' operation;

Fig. 18 is a vertical sectional view of my invention, showing the main valve in another position of"operation;

Fig. 19 is a vertical sectional View of my invention, showing 'the main valve in another position of operation;

Fig. 20 is a vertical sectional view of my inven tion, showing the main valve in another position of operation;

Fig. 21 is a chart illustrating the valve and piston motion as a 'function of time when the pump-is completely filled with liquid .and the valve is 'arranged to govern 4in a position vto give'onehalf speed at full pressure;

Fig. 22 is a chart showing the operation of my invention when the pump cylinder contains only about 15% Ysolid fluid operating at `one-half speed at Afull pressure; and

Fig. 23 is a'chart showing the operation of my invention `when the pump cylinder contains no solid fluid ybut 100% gas, operating at Aone-half speed at full pressure.

Referring to the drawings, Figs. l, 2, and 3 Ashow a fluid-operated pump 25 having an upper fitting 26 by which the fluid-operated Apump is secured to the lower end of a 'fluid supply tubing 21 by which operating fluid under relatively high pressure is delivered to the motor section ofthe fluidoperated pump. The fitting 26 has an `internally threaded portion 28 adapted to receive the upper threaded -end of a valve body 29. The valve vbody 29 has an axial minor -bore 30 formed in the upper part thereof, which is separated by a circular channel 3| from a major lbore S2 axially formed in the lower portion of the lvalve 'body 29.

Substantially intermediate between the ends of the minor bore 39 is an upper circular channel 33 which intersects the upper ends of primary fluid passages 34, best shown in Fig. 4, such uid passages extending within the wall of the valve body 29 to the lower end thereof. Spaced below the channel 3| in the major bore V32 is a iluted annular channel 35, the flutes of which intersect with the upper ends of secondary fluid Vpassages 36, as best shown in Fig. 6, each of which extends .view taken on the longitudinally to the lower end of the valve body 29, the secondary duid passages 36 being spaced between the primary fluid passages 34.

Connecting the circular channel 3| with the exterior of the valve body 29 are a plurality of circumferentially 'spaced motor discharge ports 3l, and an upper valve discharge port 38 is provided in the wall of the valve body 29. Extending upwardly from the bottom of the valve body 29 is a valve exhaust passage 39, best shown in Figs. l, 8, l1, and l2, the exhaust passage being disposed between two of the secondary fluid passages 36, .thepassage 39 also being intersected by the upper valve discharge port 36, as best shown in Fig. 8, and connecting at its upper end through a radial port 40 with the channel 3|, as best shownin Fig. `5.

The lower end of the valve body 29 is provided with a threaded portion 4| to which is threaded the upper end of a motor cylinder 42. The motor cylinder 42 is vprovided at its upper end with a counterbored annular chamber 43 fin which is disposed a plug body 44 held in fluidtight engagement with the lower end of the valve body 29 and in fluid-tight engagement with the upper Iend of a motor cylinder liner 45 when 'the parts are assembled as shown in Fig. 1. Mounted in the upper part of the plug body 44 is a valve liner 46 having an upper sleeve portion 41 extending upwardly within the major bore .32 of the valve body 29 to a point a short distance below the fluted annular channel 35.. there being an annular space 48 formed within the major bore 32 around the upper sleeve portion 41 of the valve liner 46. The valve vliner 46 is provided with an axial bore 49 therethrough, vin which is formed an annular channel 59 communicating vthrough a plurality of upper liner ports 5| with the annular space 48 when the parts are in the position shown in Fig. v1. Below the channel 50 'in the bore 49 of the valve liner v46 is an annular channel 52 which communicates through a plurality of intermediate liner ports 53 with the annular space 48. A collar 54 is formed-on the valve liner 46 ina position to rest upon the upper end of the plug body 44, the outer periphery of the collar 54 making a fluid-tight t with the lowerr end of the major bore 32. In the '-bore 49 of the valve liner 46, below the annular channel 52, is formed a lower annular channel 55 which communicates through aV plurality ofalower'liner ports 56 Vin thewall of .the valve linerl 46 with an annular space 51 surrounding a lower reduced portion 5B of the collar 54, the space 5l communicating through a radial opening 59 in the lower end of the valve body 29 with the valve exhaust passage 39.

Slidable -within the valve body 29 is a main valve member 69which is of tubular form 'and whichhas an upper Yminor portion 6| vwhich iS separated by an annular shoulder 62 from a lower major portion 63. The minor portion 6| of the valve member 6U is of .a-smaller diameter than the major portion 63 thereof and has an external surface 64 which forms a `substantially fluidtight sliding fitin the minor bore 3U of the valve body 2 9. The major portion63 of the valve member has an :external surf/ace 65 which forms a substantially fluid-tightsliding fit with the major bore V32 -of the valve body .29, the major portion of the Vvalve member extending downwardly into the annular space 48 betweenlthe major bore and the .external surface-of the valve sleeve 4l. `'The ated-65T valve member 60 is reduced in diameter to provide i of the major portion 63 of the valve member 60.

are vertical channels 13 which, as shown in Figs. 1 and 13, communicate with the annular channel 69. Likewise, vertical channels 14 are formed in the major portion 63 of the valve member 60 and communicate with the lower inlet portsA 61.

through the channel 68. The channels comprising each ofthe sets of vertical channels 13 and 14 are of varying lengths, as illustrated in Fig. 13,1

for a purpose to be described hereinafter.

Formed in the bore of the major portion 63 oi the valve member 60 is an annular channel'15 communicating with the lower inlet ports 61. Also formed in the major portion 63 is ahelical passage 16 of relatively small cross-sectional area which communicates between the annular channel 15 and a wide annular channel 11 therebelow.-

In between the threads of the lower e'nd of the helicalpassage 16 is an upper governing port 18 which communicates witha circular channel 19 formed on the exterior surface of the major portion `63 of the valve member 60. At the lower end of the wide annular channel 11 is a circular channel 80 which communicates with the annular space 48 below the valve member 60 through longitudinal valve passages 8|, and which also communicates through a lower governing port 82 with a circular channel 83 formed in the outer surface of the major portion 63 ofthe valve member.' Formed in the outer surface of the upper sleeveportion 41 of the valve liner 46, above the upper...

liner port 5|, isan annular 'channel 84, and communicating between one of the secondary passages 36 and the interior of the major bore 32 of the valve body 29 is an outer governing port |65.

Slidable within the bore of the valve liner 46 in iluid-tight relation therewith, ,and movable within the bore of the valve member 60 in spaced relation thereto, is a pilot rod 36, the lower end ofv which is connected to the upper end of a motor piston 81 adapted to be reciprocated within the' motor` cylinder liner 45 of the motor. cylinder 42.

A cavity 88 formed in the lower end of the plug body 44 constitutes a continuation of the bore of the cylinder liner 45, and is provided with an inwardly tapered wall portion 89 having an an-. nular channel 90 formed therein which intersects..

the lower ends of a plurality of vertical passages 92 formed in the plug body 44, each of the vertical passages 92 being axially aligned with' the primary passages 34, the upper end of each of the vertical passages 92 registering with the lower end of one of the primary passages 34. The cavity 88 above the annular channel 90 forms a dashpotA chamber for holding a body of iluid to stop the upward movement of the power piston 81 with a cushioning effect, as is well known in the art. As will be noted, the secondary fluid passages36,"

which lead downwardly from theuted annular channel 35, connect with iluid passages 93 having the form of grooves in the external face of the plug body 44,` the lower end thereof communicating with the annular chamber 43.

cylinder liner |06.

As shown'in-Fig. 2, the lower end ofthe motor I; cylinder 42 is connectedbythreads 95 toan in-.-

termediate plug 96 `which'ha's an upwardly.` extending tubular projection 91, the upper end of which engages the lower end 98 of the cylinder;

liner 45 in fluid-tight engagement. In the upper endoi the tubular projection 91 is a dashpot cavity 99 vfor a purpose similar to that of the cavity 88,-.the upper end of the dashpot .cavity 99 communicating through lower motor cylinder ports |00 with an annular space |0| around the tubular projection 91 and within the .motorcyl.

inder 42, the upper end of which communicates, as shown in Fig. 1, through longitudinal passages |02 formed between themotor cylinder 42 and.' lower end of the the cylinder liner 45 with the annular chamber 43. Y

The lower portion of the intermediate plug 96 is provided with external threads |04, to which is threaded the upper end of a pump cylinder |05 having a cylinder liner |06 therein, similarly to the motor cylinder 42 with its liner 45 therein,

vertical longitudinal passages |01 being 'providedi" between the pump cylinder-and the .cylinder liner. Disposed between the lower end of the in'- termediate plug 96 and the upper end ofthe cylinder liner |06 of the pump cylinder |05 is an'- upper pump valve device |08 which includes an upper discharge valve 0 and an upper. inlet valve The upper discharge valve H0 is housed in a chamber |2 formed in the lower endl of the intermediate plug 96, which communicates through upper discharge passages ||3 with the exterior of theintermediate plug 96, the upper;

discharge valve including a spring-held ball member" |4 adapted to open inwardly to permit allow of fluid from the upper end of the cylinder,

liner |06 therethrough and through the upper discharge passages ||3, but preventing atreverse flow. The upper inlet valve is disposed ina chamber ||5 provided in a valve cage ||6, and

includes a spring-'held ball member ||1 adapted to open downwardly to permit a ow of iluid into-- the upper end of the cylinder liner |06 through an upper inlet passage I8 formed in a valve ring` |9disposed between the lower end of the in. termediate plug 96 and the upper end of the valve cage ||6.

An intermediate piston rod |2| extends down. wardly from the lower end of the motor piston 87|A4 through a sleeve |20 in the intermediate plug '96 and through the upper pump valve device |08, and has its lower end connected to a pump piston |22, the 'pump piston being reciprocable vin the As shown in Fig. 3,the lower end cylinder |05 is provided with internal threads |23 by which the samev is connected to -a lower' plug |24. Between the upper end of the lower plug |24 and the lower end of the cylinder. liner? |06 is disposed a lower pump valve device |25@- which includes a lower discharge valve |26 and' a lower inlet valve |21, the lower discharge and inlet valves |26 and |21, respectively, being simi- ,-lar in -construction to the'upper discharge and' inlet valves ||0 and respectively. Thelower:

discharge valve |26 communicates with the lower end of the cylinder liner |06 and with a lowery discharge passage |28 formed in the lower plug. |24, which in turn communicates with the ex-.-

terior of the plug. The lower inlet valve |21 communicates between the interior of the lower end of the cylinder liner |06 and with a .space |29 between the exterior of the lower pump valve.

`device |25 and the pump cylinder |05thespace of the pumpy assenso The lower en'dr of; theY lower plu'g' |24"n Isl con; riectedf by 'external threads to ailower' inlet iittinsr l'lfprovided with a lowerv conicali erld |32A irl' 5, which-'a'ninlet opening* |'33isAV formed. 'I'llecoriil carene. |32 of the lnlet'flmng' |31 eul'eptedA te' seat ih'fa'ninletrseat |34 carried'by'a'bottoinholef" fttil'igl |35 suitably threadedf-'to' thef lower endI of-I a'1pio'duction`tubing'- |36 whichrextends'upwardly 10 throughpthe wellfto' they surface of the' ground' aridi-'isi adapted to convey pumped' fluid there# through. I: preferv to" connect'to' the' lower end'v ol'-Y the` fitting` |35" a` liner |31 having: a lower' open'" eiid-` and which` may extend asy far as`l desiredy 1n below' ,the tlttlngr into the' wellpalthoughfit will.' be understood that this liner may be'omittedifI d'esilled; l

:Threaded into thel lower end'of thelower plug |2'4 is" `a tubular closure member |38 having itsigg lowerendfolosed. A lowerpistonrodl |39'srsuitablyfconnctedfto the lower end of'thepumpfpis# tonI |22' and' extends-,downwardly through thelower pump-valve device |25 and-thelower plug |-24into the-interior of' the tubular closureinem-'-y 2;,- ber"y |38. As willbe ntedxthepilotrod'8B;thef motor ."pistoxiv 8-1', the interm'ediate piston" rod' |2|, th'erpump'-piston |22; andthe lower piston rod' |39-` are provided withl axially aligned' and communicating longitudinal' passages |4|, |42,u 30 V43; |443 and' |455- resp'e'ctively, l'so'as to'provide iluid "communication therethrough withvv the in`- terior' o'fthe tubular'. closure' member |38 so asito balance; the fluid'. pressure ori' vthe' upper and" lower end'softhefrods.

A'sfshown in Figs'. 1 and 4,' the' upper'end ofthe' pilot" rod 86' providedwith a* plurality ofcircuiii'fe'rentially' spaced upperv vertical' channels" lli-arid also formed therebelow in'the'" exter' nalI surface of the pilot rod' is' a' set'of lower' 4o' vertica'ltchannels* |48, asbestshownin'Figsrl: and'l 1 2;I fer a' pl'lrpo'se"1 to be described' hereina after.

During operation,l i operating fluid; such "as: for' exa-inplci'oil, under relatively' highpressure"is5 conveyed downwardlythrough the' fluidisupply' tubing' 2'|` and-the upper fitting 26 to the interior l of the valve body 29, from whence itis conveyed throug'hthe main valve member' 60, ras will be described hereinafter', alternately' to" opposite- 5u ehdsfofthemotor piston 81, causingthesanle"` to reciprocate' in the cylinder liner" 45:` 'Rec'ipro' catin1of the motorpiston 81 is communicated' through theintermediate'piston'rodr |2'| 'to the pump` piston 22, causing the san'ie Ato reeipro'ca'te' 55 similarly. inthe cylinder'liner |06.' In'thefposition' shown in Fig. 1, theun'otor' pistor'ial is sub"'v stantially at `the-upper end of its'stroke' and as'' itxn'oves' downwardly to the position' sho'wnfiri` Figi" 17,' 1in' 'which it is 'substantially' at'the'-lower.`- 60 ed o'ff its" stroke, it'.`A carriesl with, it the pump piston l 2 2 f and well fluid flows 'upwardly' tlirongh theA liner |31`,thefinletopeiiing |33; the'ilower irllet'-lltting` |3|, thevertical inlet passages |30;V the space'z 2 9; theA longitudinal 'passages 01, and# 65 the'upper inlet passages H81 through the' upper inletv valve l |,.v and f into' the' upper ende of th'e cylinder" liner' |06'ab'ove thepump piston.' |22 as: the'saulemovesfdownwardly;A During such-dowll'i'-' ward movement of the'pumpp'iston |22",` fluidi, in the cylinderA liner 'i |116'Y therebelovlf` is expelled therefrom ith'rough the "lower discharge'ivalve'" 2 6 adthelower discharge passagel28fdireo'tlyfin ff the=`-preduetien tubing' |36; from-wlle'n'eelt'fllewsi up'wrdly therethrough to'LIV the'f" surface* ofj" the? 75" effxiu'. During leweweeemovemetj er the pump pieren-1221; obviously, ,the-upper' discharge reialnel'ese'dz wlent'hemeter pieten s1 starts its? upward" stroke' from the' position shown in' space-"|29- willl be" drawn inwardly through the.'v

lower inlet valve' vl'zfmte the lew'er end ef the' cylinder liner' los Below the pump piston |22, er1-elet the 'same tuile fluid in the4 cylinder liner mefabeve tue-'pump'.pisten |'22 wi11 be expelled therefronif-throu'gh'the upper discharge'valve' |||lV al'l'lh'eY upper discharge passages H3' int-0' the pielflueu'en` rubin-'g fst; freni' whence' it newsI upT4 waidlyto'thesuriace ofthe` ground.' Thus,=it' will be'd'n'deistoo'd that' aisubstantially continuous ubwa'rdf new' of pumped nel@ ere'ete'd mme' production tubing'Y |135' during recipr'ocat'ion' of el'itly-Y under di'fferentwell7` conditions its normal' operation under n'ornia'l well'c'onditions will-first be' described.'

inder liner |06' is lled with substantiallysolid uidL'iL' e., when' thereis'littleorlnofreegas mixed with the liquid iti the cylinder 'liner 05. When'- thef'pum'p cylinder liner |U6is entirely lilled'with liquid,` r the operation is` the" saine whenV the valv'e member" 60 is'designed togov'e'rn at' full speed atiull' pressureI asA for half-speed or any other speed.l Consezquently, the following description will'serve' to-il1ustretethe operation' of the'device under normalconditions'; regardless of thespeed provided for dui'ng governing. 'The'y pump discloseclhereinfisdesigried to operate at half-speedl atv full pressure? o'ftheoperating iluidi during governing;l A' y With'the part'siin'the'lpos'ition shown in Fig; 1j

the' main* valve member SUfis' in itsvupper'most" positionfand'thefmotor and pump pistons 8l and |22', respectively', andi the" pilot rod 86; have reached substantially' the' upper ends of their upwardstrokes. Thev lower inlet'ports 6T of the" .mainvalvemerriber are aligned with the"i'lu'ted annular' charin'el'35 and a'lfe fully open,- vand there isianunres'tricte'd 'iiowof'' operatingM fluid from the" supply' tule-lne-A througli;the-interim" er' the valve' body' 2 9and'through'tlielower"inlet' ports 461', the y chamber" 43; theiolig'itlldina'l passages |02, and

the' lowerfmot'or cylinder' ports" 00j into 'the' ',c'ylin delliner"45"bel'ow tlle'moto' piston 811 tenf'lingfto cause' the' saine' to" moveu upwardly. The* upper end'oi" the mo'tor`pisto'nf81 isopentothe' rela-v tively low'` fluid pressure in" the production tub? irlg |3|i`,:the samehe'ing" called discharge pre's sure hereinafter, through the annular channel 90, the' verticali passages' 92'.: the primary fluid' passages' 34'; the circular channel 33", the-annular" channel 69:'an`d the' m'oto'r discharge portsl;

l By normal well' condtions vIA meanfth'e usual situation'in'which the puni'p cyl'-A beneath the main valve member 60 to discharge pressure through the intermediateliner ports 53, the annular channel 52, the lower vertical channels MB, the lower annular channel 55, the lower liner ports 55, the annular space 51, the opening 59, the exhaust passage 39, the annular channel 3|, and the discharge ports 31 to the exterior of the valve body. Since the pressure exerted by the operating uid on the upper end of the minor portion 6| of the valve member 60 is substantially greater than the pressure exerted on the lower end of the major portion 63 of the valve member by the discharge pressure in the production tubing |36, the valve member, as shown in Fig. 1, is about to move downwardly. The valve member 60 then moves downwardly at a relatively high rate of speed to the position shown in Fig. 14, at which time the downward speed thereof is materially reduced, the initial phase of the downward movement of the valve' member being graphically represented by the-portion |50 of the chart illustrated in Fig. 21.

As the valve member 60 movesv downwardly from the position shown in Fig. l to the position shown in Fig. 14, the lower inlet ports 61 therein pass out of registry with the fluted annular channel 35, thus shutting off the flow of operating fluid to the lower end of the power piston 81. Similarly, the annular channel 69 formed on the exterior of the valve member 60 passes out of registry with the circular channel 33, thus shutting off the exhaust ilow of spent operating iiuid from the upper end of the motor piston 81.

When the valve member 66 reaches the position shown in Fig. 14, the lower end thereof has just closed the intermediate 'liner ports 53 so as to shut oi the open exhaust of fluid therethrough from the lower end of the annular .space 48. However, just prior thereto downward movement of the valve member 60 has caused the annular channel 68 to register with the upper valve discharge port 38, so as to maintain the annular space 48 below the valve member in communication with the discharge pressure through the valve passages 8|, the circular channel 86, the wide annular channel 11, the helical passage 16, the annular channel 15,-the lower inlet ports 61, the annular channel 68, the upper valve discharge port 36, the exhaust passage 36 and the valve discharge ports 31. Since the helical passage 16 is relatively long and is of restricted crosssectional area, uid from the space 48 below the valve member 6B exhausts slowly, and, consequently, the valve member 6D moves slowly un` til it reaches the position shown in Fig. l5, this slow phase of its mov-ement being graphically illustrated by the portion of the chart shown in Fig. 2l.

During the relatively slow downward movement of the valve member 60 between the positions shown in Figs. 14 and 15, the ilow of operating iluid to the upper end of the motor piston 81 is started and increased gradually to prevent iiuid shock which would otherwise occur if the full Volume of operating fluid were suddenly delivered to the motor piston. This gradual increase in the volume of operating ilui-d delivered to the upper end of the motor piston 81 is controlled indirectly by the varying-length vertical channels 13, best shown in Fig. 13, which, as downward movement of the valve member 60 progresses, successively open restricted duid communication between the relatively low discharge pressure in the ports 31 and the circular channel 3|, and, consequently, the lower end of the motor piston. The throttling eiect of the channels 13 only gradually relieves the iiuid pressure on the lower end of the motor piston 81, which retards the movement of the piston. Consequently, the motor piston 81 accelerates gradually in its initial downward movement, as graphically indicated by the portion |66 of the chart of Fig. 21. It will thus be understood that during the first portion of this slow phase of the downward movement of the valve member 66 the discharge from below the motor piston 81 is metered by the vertical channels 13.

As soon as the vertical channels 13 start to register with the lower circular channel 35 and spent operating fluid ows therethrough from the lower end of the motor piston 81 with the downstroke thereof, the pilot rod 86 also moves downwardly to take the lower vertical channels |48 therein out of registry with the annular channel 52, as shown in Fig. 15, thus shutting off all .communication between the annular channel 52 and the lower'annular channel 5 5 during the remainder of the downstroke of the Valve member 60. However, upon the valve member reaching the position shown in Fig. 15, the cirf cular channel 19 registers withthe outer governing port |65, and the lower end of the valve member 60 is thus additionally opened to discharge pressure through the upper governing port 18, the outer governing port |65, the secondary passage 36, the uted annular channel 35, the vertical varying-length channels 13, the shallow annular channel 69, and the motor discharge ports 31. The cross-sectional area of thisA fluid path and the length of this path are selected to give a fluid flow capacity which is large relative to that of the path through the helical passage 16, the valve member 60 increases its downward rate of movement until it reaches the position shown in Fig. 16, this phase of downward travel of the valve member being graphically represented by the portion |52 of the chart shown in Fig. 21. As will be noted from Fig. 21, however, the downward speed of the valve member 60 during the portion |52 of its travel is not as great as the speed of its initial travel rep-y resented by the portion |50, which is due to the difference in lengths and cross-sectional areas of the passages and ports through which the fluid exhausts from the annular space 48 in the two portions of travel of the valvemember, respectively.

It is to be noted that on nthe downstroke of the valve member 60, although the annular channel 65al initially registers with the circular channel 33 simultaneously with the initial registry of the vertical channels 13 with the uted annular channel 35 so as to throttle the initial discharge of spent operating fluid from below the motor piston 81, the annular channel 65a on the upper end of the valve member 60 fully opens to the circular channel 33 before the annular channel 69 fully opens to the fluted annular channel 35.

As soon as the annular channel 65a registers with the circular channel 33, a substantially uninterrupted flow of operating fluid can ilow to the upper end of the motor piston 81, and thus the vertical channels 13 continue to throttle the ilowD of spent operating uid from vbeneath the motor piston after a free flow of `operating fluid is permitted to flowA to the upper end of the motor piston. This continued throttling of the spent operating uid through the vertical channels 13 only continues, of course, until the valve member 60 has moved downwardly sufliciently to permit tion shown in Fig. 16, it will be noted that'the i i circular channel 19 has passed downwardly out of registry with the outer governing portY |55, and, consequently, lluid from the annular space 4 8 must again exhaust through the helical'pas Vsage 16 and the upper valve discharge port 33,

which, due to the relatively small fluid flow capacity of this path of flow, produces a small amount of end movement of the valve member at the same'rate as represented by the po1tion"`|5,i of the'cha'rt vof Fig{2 l. This slow end action of thevalve member is designed to protect it against undesirable hammering,A and ffor'the purpose' of simplification has been omitted from the 'charts of Figs.'2l to 23, although it will beV understood that it will be'present under allv onditions' o f operation where the valve ymember eompl'e'tes its stroke. So far as a general understanding of the action of the valve member 6l) isconcerned, how'- ever, the valve member may be regardedas'fremaining substantially inthe position shownl in Fig. 1 6 until it starts itsupst'roke, this stationary phase of the valve members action `being shown by the portion |53 of the chart of Fig. 21.- As will be noted, when vthe valvemember 6;) reaches theV position shown in Fig'. 16, operating 'fluid unrestrictedly flows to the upper'end of themotor piston 81 from lthe uppeifitting 23 through the annular channel 55a'and the upper inlet ports 6 6, through the circularchannel 33,'the primary fluid passages 34, the passages 92, and through the 'annular chanel Si] into the ,upper end of 'the cylinder nner "45. 1n' uns position, al'so.' the lower end of the motor piston 81 is u nre`s ictedly opened to exhaust lpressure through' the oit/ er motor cylinderv ports |00, the longitulinalpas- -v sages |02, the annularI chamber 43,'y the fluid passages 93, the secondary fluid passageslifthe uted annular channel 3 5, the annularchannel B9, and the motor discharge portstfl. The motor piston' 81 then'compl'etes its downwardfstroke,

graphically represented by the portion ll'iflof` chart of Fig. 21, reaching the positionsh'o'wn in Fig. 17.

When the motor piston 8 1 and pilot rod 8 6 approach theirv lower position, shown Figfl'l, the upper longitudinal channels" I 4fo` pilot rod register with the annular channel 5D"iri'fthe upper sleeve portion 41 of the va-lve'liner as to open fluid communication between theoperatingV fluid' in the supply pipe 21 'and4 thelowei end of the space 48 through the'an'nular channel 5D, the upper liner portsI, the'wide annular channel 11, the cireular'channel S, and the valve passages 3|. Since the cross-seetional areal of the lower end ofthe valve member 6l! is (greater than that of" its u'pper end, and since the valve member 60 is so designed that `when in this position the total upward force exerted' bythe'fperating fluid thereon exceeds the't'ot'al downward force exertedrthreon by the operating'fluid and the discharge pressure, the admission of operating fluid beneath the valve member 6 0 causes the same to move upwardly' at a relatively high rate of speed to the"positionshown' in Figfl, this first phase o 'the'upward movement of the vvalve member being graphically illustrated by the portion |55 ofthe 'chart shown in FigfZl'. It will be understood that the area ratio between the pressure ends ofthe valve member 6|) Vwhich includes the areas open to exhaustI can be altered to vary the action of the valve member as desired.

In the form illustrated, the upper portion of the valve member 6| l is divided into two equal pressure cross-sectional areas by the sliding nt of the minor portion 6| thereof in the minor bore 30, i. e., the .upper end of the'valve memberll, a cross section of which denes one of such areas, and the top of the major portion 6 3 of the valve member, a cross section of which defines the other of such area-s. This is accomplished by selecting the diameter of the minor portion 6| so that its cross-sectional area, less the cross-sectional area of the valve sleeve 4 1, is equal to the Vcross-sectional'area of the major bore'32 less the cross-sectional area of the minor bore 30. Also, in this case, the cross-'sectional area of the major bore 32, less the cross-sectional area of the valve sleeve 41, is equal to the sum of the two net areas set forth' above.

' "Upon its arrival at'the position shown in Fig.

18, the lower end of the 'valve member 6 0 has just closed the upper liner ports 5|, but considerably previous thereto the annular channel 1 5 has opened fluid communication between the operating fluid and the annular space 43 through the helical passage 16, the wide annular channel 11, the circular channel 80, and the valve passages 8|. Thus, closure of the upper liner ports 5|V does not stop the upward movement of the valve member 60, but due to the restricted crosssectional area and length of the helical passage 16, the flow of operating fluid to the underside of the valve member is retarded, and, consequently, the valve member moves relatively slowly to the position shown inFig, 19, this second phase of thev upward movement of the valve member being graphically illustrated by the portion |56 of the chart of Fig. 21. It is to be noted that when the valve member 60 travels upward before the lower inlet port 51 is out of communication with the upper valve discharge port 38, the upper end of the helical groove 16a is open to high pressure operating fluid above the'valve liner 4B. This is an' important feature, as occasionally the pilot rod 86 may move upwardly slightly so as to move the upper longitudinal channels |48 therein out of registry with the annular channel 50, which stops the ilow of operating fluid to the lowerl end of the annular space 48 through the upper liner ports 5I, but in this case the'helical groove 16a is open to high pressure before the ports 61 are cut off lfrom the port 38, and therefore the valve member 60 cannot stop on dead center. This is accomplished by having the pressure open through the helical groove 16a, and exhaust open through the ports 61 and 38 for that part of the motion of the valve 60 where dead center would otherwise be possible. If the pilot rod 86 moves upwardly slightly so as to move the upper longitudinal channels |45 out of registry with the annular channel 50 while the lower inlet ports 61 are still in fluid communication with the upper valve discharge 38 through the annular channel 68, since fluid communication still exists between the lower end of the space 48 and the discharge pressure through the helical passage 16, the fluid from below the valve member will slowly exhaust therethrough, permitting the valve member to move downwardly to the lower vso as to move the upper longitudinal channels |46 out of registry with the annular channel 50, f'. after the upper end of the annular channel -10 has moved above the upper end of the valve linerv' 46, operating fluid is then in direct communical.V

tion with the lower end of the valve memberV .l

through the helical passages 16 or 16a, and itl' can complete its upstroke at the rate indicated115 by the portion |51 of the chart of Fig. 2l. The same feature to eliminate the tendency of the l valve member -60 to stop on dead center is proj-'f vided in the downstroke of the valve member 60"' when the lower inlet ports 61 move downwardly-:.20 out of communication above the valve liner 4Q. with the operating fluid and before the annular;l channel 68 registers with the upper valve disv: charge port 38. The helical groove 16a, is open`r` to pressure and hence eliminates any tendency of, the valve member to stop on dead center.

During the relatively slow upward movementof the valve member 50 between the positionsV shown in Figs. 18 and 19, the flow of operatingL fluid to the lower end of the motor piston 81 is 30 :started and increased gradually to prevent fluid jshock which would otherwise occur if the full volume of operating fluid were suddenly delivered to the motor piston. This gradual increase in the volume of operating fluid delivered to the lower end of the motor piston 81 is controlled by the varying-length vertical channels 14, best shown in Fig. 13, which progressively register `with the uted annular channel 35, to meter the ,flow therethrough. Consequently, the motor pisl,ton 81 accelerates gradually in its initial upward movement, as graphically represented by the portion IBI of the chart shown in Fig. 21. Simultaneously with the initial registry of the vertical channels 14 with the fluted annular channel 35, 4,) the annular channel 69 of the valve 60 starts to uncover the annular passage 33 in the valve body, which communicates through the channel 69 and discharge ports 31 to exhaust pressure and opens the upper end of the motor piston 8l 50 to discharge pressure simultaneously with the initial admission of operating fluid to the lowerY end of the motor piston. The vertical channels 14 are of such length that on the upstrokeof the valve member the annular channel 69 fully 55 registers with the circular channel 33 to permit uninterrupted discharge from the upper endf the'motor piston 81 while the vertical channelsA I4 are throttling the flow of operating fluid therethrough to the fluted annular channel 35 60 and to the lower end of the motor piston.

When the valve member B0 reaches the posi,- ticn shown in Fig. 19, the circular channel 83 and the lower governing port 82 register with the outer governing port |65, and the lower end of 6 the valve member 60 is thus additionally opened to operating iiuid through the lower inlet ports 51, the fluted annular channel 35, the secondary passage' 3B, the outer governing port |65, the lower governing port 8.2, and the valve passage 8|, and thereupon the valve member continues its upward movement at an increased rate-pf speed until it reaches the position shown in Fig; 20.v vThis phase of upward movement of the val-ve :s

the circular channel 3| and the motor dischargeA ports 31. Also, the lower end of the motor piston 81 is unrestrictedly opened to operating fluid through the lower motor cylinder ports |00,'the.

longitudinal passages |02, the annular chamber 43, the fluid passages 93, the secondary fluid passages 36, the fluted annular channel 35, and the lower inlet ports 61. Consequently, from the position shown in Fig. 20 the motor piston 81 moves upwardly to the position shown in Fig. l, as illustrated by the portion |59 of the graph of Fig. 2l. When the valve member 6D has moved upwardly to the position shown in Fig.r 20,'lt will be noted that the upper end of the valve member has not yet engaged the fitting 26 and that the annular channel 83 has just moved out of registry with the outer governing port Consequently, in this position operating fluid can still ow to the lower end of the valve member 60 through the helical passage 16, which causes a slight further end movement of the valve member at a reduced rate of speed, which is the same as that indicated by the portion |56 of Fig. 21, and which provides a small amount of upward end movement of the valve member similar to the lower and movement thereof described hereinabove. So far as a general understanding of the operation of the valve member 60 is concerned, the valve member maybe regarded Ias remaining substantially stationary in the position shown in Fig. 20, as graphically indicated by the portion |58 of the chart of Fig. 21, the remaining upward movement of the motor piston being represented by the portion |59 of the chart. When the parts reach the positions shown in Fig. l, a complete cycle of operation has been completed, and a new cycle starts, as described hereinabove. Y

From the foregoing description, it may be noted that if any sand is carried upwardly with the well production through the production tubing |36 it cannot readily enter the valve element-25 so as to damage the valve 50, as it must pass through the discharge ports 31, the annular channel 3|, the vertical passage 39, and the port 38. Such passages provide a tortuous path deterring the entrance of such sand, and this is a. feature of the invention, as the presence of sand may obviously be detrimental tothe operation of the valve `60.

In the operation of a fluid-operated pump, such as described herein, it is desirable to main- .tain the flow of operating fluid to the motor piston at a substantially uniform rate. If, however, the pump load is suddenly decreased, the rate of flow of operating fluid normally would increase, as pointed out hereinabove, with at- 5 tendant excessive increase in the speed of the motor and pump. To prevent this condition occurring, my invention includes governing means adapted to operate in response to a decrease in pump load to maintain the flow of operating iluid to the motor piston 81 below apredetermined maximum rate, so as toA preventundesired acceleration of the moving parts, and the operation of such governing means is now described.

The governing means of my invention includes .tion |59 of Fig. 21. continues its downwardmovement at a slow rate,

lby the portion of Fig. 21.

-iluid passages 36 and the annular space liyas shownfin Fig. 10.

'operante with 15% liquid When the pump cylinder liner |03 aheadof ,the pump piston |22 contains onlyabout 15% well liquid and-the balance gas, the governing actionlof my .device is as follows: The valve member ,60 moves downwardly from the position shown in Fig. 1 to the position shown in Fig. 14

at-a rapid rate, this portion of its movement being illustrated graphically by the portion |52 of the .chart of Fig. 22, which action is exactly .the s ame as the action thereof shown by the por- The valve member 50 then this portion of its travel being illustrated by the portion |63 of the chart of Fig. 22which action is .exactly the same as the actionthereoi shown At the beginning of the slow downward movement of the valve member 6D, in which it is in the position shown in Fig. l5, the channel 65a begins to register with the circular channel 33 to permit an initial ilow of operating fluid from'the supply pipe 21 to theY upper end ofthe motor piston 81, and simultaneously during this portion of the move- 'ment of the valve member 6G the vertical chan- "nels l1,3 successively register with the iluted annular channel 35 to permit a restricted flow of spent operating fluid to exhaust from below the motor piston 81. After the vertical channels 13 begin to register with the fluted annular channel-35, at which time the annular channel 65a ,is fully'open to the circular channel 33, `the circular channel 19 registers with the outer governin g port |65. Since the pump cylinder liner |113 v, 'below the pump piston |22 is lled largely with the downward movement of the motor and pump pistons at a greater rate of speed than would be the case if the pump piston were engaging solid liquid; Due to the fact that the discharge from below the pump piston is throttled by the restricted cross-sectional areas of some of the vertical channels 13 communicating with the fluted lannular channel 35, nuid pressure quickly builds vupin the secondary passages 3G, and this rise in fluid pressure is communicated to the lower end of the valvermember 6U through the outer -governing port |65 and the upper governing port 18, which prevents further downward movement of the valve member until the fluid pressure therejbelow is reduced, as the valve member is so de'- signed that a predetermined rise in pressure therebelow will stop its continued downward movement, due to the difference in areas of its upperand lower ends, and due to the fact that fluid under such increased pressure is supplied from the secondary passage 35 through the outer governing port to the bottom' of the annular space- 48 faster than it can exhaust through the ,helical passage 16. This portion of the valve cycle, during which it hangs up and meters the now, may -be referred to as the governing portion of its cycle, and is represented by the portion |6311 ofthe chart of Fig. 22.` It is also to be 'notedithat the proper relation'must ,be'maintained in design between the Vcross-sectional area of the outer governing port 1165, the Ahelical passage 16, the annular channel 1.9, the port 1B, .the wide annular channel 11, Ithe annular channel andthe vpassages 8|, as :the outer governing port |`.5 must admit fluid tothe lower end .of the valve member -611 vfaster than vthe helical passage 15 will permit it to exhaust through the upper 'valve discharge port 138.

The motor piston 8.1 will move at the predetermined governed velocity (in this case, onehalf of the full rated speed of the pump), -as indicated by the portion |81 of Fig. 22, until the pump piston strikes solid liquid, which point is indicated at |61a of Fig. 22:. When this occurs, the downward rate of movement of the pump piston |22, and the .motor piston connected thereto, is reduced.' and consequently the iluid discharge pressure in the secondary passages 35 drops due to the reduction in speed of the pistons. thus allowing lthe uid beneath the valve member 60 in the annular space 48 to exhaust into the secondary passages 3B through the outer governing port |65 to permit the valve member to resume its downward movement from the position shown in Fig. 15 to that shown in Fig. 16, which movement is represented by the portion |68 of the chart of Fig. 22, and which is exactly the same as the corresponding valve movement under normal conditions as represented by the portion |52 of the chart of Fig. 21. During the rst part of this movement of the valve member 6|] from the position shown in Fig. 15 to that shown in Fig. 16, the vertical channels 13 gradually shorten to zero length, at which time the annular shoulder 62 of the valve member 60 registers with the uted annular chamber 35. During the remainder of the movement of the valve member 60, the passage area opens rapidly as the shoulder 62 moves to the lower side 'of the fluted annular channel 35, at which time the annular channel 59 registers with the channel 35 to fully open the discharge from the lower end of the pump piston |22. Prior to the governing or metering action through the vertical channels 13, the annular channel 65a has registered with the circular channel 33 to open the upper end of the power piston 81 to operating fluid, as described hereinabove in connection with the operations shown in Fig. 21. As soon as the pump piston |22 hits solid liquid in the pump and the valve member 60 has reached the position shown in Fig. 16, the balance of the stroke of the motor piston 81 is at normal velocity, as indicated by the portion |69 of the chart of Fig. 22, the change in speed of the piston from one-half normal velocity during the governing portion of the valve-cycle to further reduced velocity at the beginning of the transition from and back to normal velocity when the valve reaches the full open position being gradual as the valve member is in the throttling or controlling position shown in Fig. 15 when the pump piston strikes solid liquid and the valve has to open before the piston can assume normal speed under load, which, plus .i the compression of the gas below the pump piston, tends to round off the curve shown in Fig. 22v and make a gradual transition in piston speed, as illustrated by the portion |6911 thereof. As soon as the valve member 6|) reaches the position shown in Fig. 16, it remains substantially stationary until the 'motor piston 81 completes its downward stroke,

this portion of the action of the valvev member being represented by the portion I1| of the chart of Fig, 22.

'I'he same type of governing action takes place upon the upward movement of the valve member 60, as is shown by Fig. 22, but is accomplished in a slightly different manner. When the pump cylinder liner |06 above the pump piston |22 is similarlylled with a mixture of gas and fluid, the upward movement of the valve member -60 is the 'same as the upward movement thereof under normal conditions of operation as shown in Fig. 21 until the valve member 60 reaches the position. shown yin Fig. 19. When the valve member 60 reaches the position shown in- Fig. 19, the upper end of the motor piston 81 is fully open to exhaust pressure by registry of the annular channel 69 with the circular channel 33, and discharge ports 31, but operating iiuid is still metered through the vertical channels 14 whichl have just started to register with the uted annular channel 35, thus throttling the flow of operating iiuid to the lower end of the motor piston 81, as described hereinabove, and the circular channel 83 of the lower governing port 82 has just registered with the outer governing port- |65. As will also be noted from Fig.'19, the motor piston 81 has started its 'upward movement, and the vertical channels |46 are out of registry with the annular channel 50. Due to gas in the pump cylinder above the pump piston |22, the uid pressure of the operating fluid in the secondary passages 36 remains relatively low as the flow is throttled through the vertical channels 14 until the pump piston strikes solid liquid, and while the pressure in the secondary passages is thus relatively low, operating fluid which would be normally supplied to the lower end of the valve member 6D through the helical passage 16 is permitted to discharge from the wide annular channel 11 through the lower governing port 82, the circular channel 83, and the outer governing port |65 into the secondary passages 36, thus keeping the full pressure of the operating fluid off the lower end of the valve member Bil, which causes it to remain stationary in a second governing position, as illustrated by the portion |12 of the chart Fig. 22. As thev valve member 68 thus hangs up until the pump piston |22 again strikes solid liquid, the flow of operating fluid to the lower end of the' motor piston 81 is metered through the vertical channels 14 while the valve member remains stationary. As soon as the pump piston strikes solid liquid, the uid pressure in the secondary passages 36 rises due to a decrease in the throttling action of the vertical channels 14 because of the resulting lower pump piston speed, and, consequently, the discharge of operating uid from the lower governing port 82 stops,l and operating iiuid then flows to the lower end of the valve member 6|) from the secondary passages 36, causing the valve member 60 to resume its upward movement represented by the portion |13 of the chart shown in Fig. 22. The upstroke of the-motor piston 81 is the same as thev downstroke, as shown in Fig. 22, when the proportion of gas and liquid;

on both ends of the pump piston |22 is the same.

Since the speed of the motor piston 81 is reduced during governing to one-half that illustrated in Fig. `2l, and since the piston moves 85% of its stroke at half-speed, it takes 1.7 times as ylong to hit solid iiuid as it does to complete the full stroke illustrated'in Fig. 21. The total time for the stroke of the'motor piston 81 depends on how constant the maximum pressure is held. If it is constant, then the remaining 15% of the stroke of the motor piston 81 will take .l5 of the normal time. Therefore, the total time for the cycle will be 1.85 times that of the normal cycle shown in Fig. 21. Of course, if the pump is operating at full pump speed and is on a source of operating fluid of constant displacement when governing takes place, then the surplus operating iiuid vduring governing must be disposed of through a suitable relief valve or the volume displacement of the source would have to be reduced an amount corresponding to thereduction in speed of the fluid-operated pump.

Operation with zero liquid Fig. 23 graphically illustrates the operation of the motor pistons? and the valve member 66 in the special case when the pump is operating at zero efficiency, i. e., when the pump is not pumping any fluid from the well. This condition of zero enciency may be caused by the upper and lower inlet valves and |21, respectively, becoming clogged with foreign material so that they will notunseat, or may be caused by other operating conditions. Under these conditions of operation, the Valve member 66 performs its rst two functions, illustrated by the portions and |8| of the chart of Fig. 23, normally, as will be seen by a comparison with the chart of Fig. 21, but hangs up and remains in the governing position shown in Fig. 15 and graphically indicated by the portion |82 of Fig. 23 for the remainder of the downstroke of the motor piston 81, indicated by the portion l82a of Fig. 23. The valve member 6|) hangs up due to the normal pressure drop in the passages due to iiuid friction therein, which pressure drop is sufficient to cause the valve member to hang up so long as no fluid is being pumped by the pump piston |22. If the condition of zero efficiency is caused by the pump cylinder being lled with gas only and the pressure on this gas is such that compression to the full discharge or column pressure occurs before the piston reaches the end of the stroke, gas will be discharged by the pump piston |22, and in this case the valve action will resemble the action thereof illustrated in Fig. 22. The point where the gas is compressed to full column pressure will rcorrespond to the point where the piston strikes solid iiuid. At the end of the downstroke of the motor piston 81, the valve member 66 then resumes substantially normal operation for its first two functions on its upstroke, as graphically indicated by the portions |83 and |84 of Fig. 23, on the start of the upstroke of the motor piston, but hangs up in the governing position shown in Fig. 19 and graphically shown by the portion |85 of Fig. 23 for the balance of the upstroke of the motor piston. It will therefore be appreciated that under such conditions of operation the speed of the piston motion is substantially reduced and the'energy of the operating fluid, which would normally be used to operate the iiuid operated pump to lift well liquid, is all consumed in the throttling action of the valve member 60.

It will be appreciated that the conditions of operation graphically illustrated by Figs. 21, 22, and 23 are not mutually exclusive or typical, but are merely examples of the operation of my invention under selected different operating conditions selected for illustration. The movement of the valve member 60 under other operating conditions may vary substantiallmbutl in every case will be such as to meter the flow to the motor piston B1 on the upstroke of the valve member and to meter the ow from the motor piston` on the downstroke of the valve member, to prevent racing of the pistons. Those skilled in the art will readily understand that the ow governing action of my Valve construction occurs whenever the pump piston |22 strikes gas instead of solid liquid, and that the upward or downward movement of the valve member 60 stops until the pump piston strikes solid liquid, thus providing an automatic throttling action to maintain the ow of operating uid to the motor piston 81 below a predetermined maximum rate, thus preventing racing. of the pump with the attendant danger of damage to the moving parts. It will thus be apparent that the number of strokes per minute of my pump will be maintained below a predetermined maximum, regardless of the presence of gas inthe pump liner |06 and regardless of the amount of such gas, in spite of the normal tendency of the pistons to speed up under such circumstances.

Therate of speed of the motor piston 814 during the governing portion of the cycle of the valve 6U may be changed readily by changing the width of the circular channels 19 and 83. If it is desired to cause the. motor piston 81 to travel at a slower speed during governing of the valve 60, the channels 19 and 83 are merely widened so that they open earlier and hence at a point where the available cross-sectional area of the vertical channels 13 and 14 is smaller. If it is desired to cause the motor piston 81 to travel at a higher speed during governing, the circular channels 19Y and 83 are merely made narrower, so that they open later at a point where the availablev cross-sectional area of the vertical channels 13 and 14 is greater. The speed of the motor piston 81 during the governing portion of the cycle of the valve 60 is a direct function of the available cross-sectional area ofA the vertical channels 13 and'14 at the start of the governing portion of the cycle, anda square root function of the applied pressure. It will thus be understood that the present valve construction has considerable versatility and can be made to control the operation ofr the motor piston S1 under a variety of pumping conditions as desired.

It will also be understood that, although in Figs. 21, 22 and 23 I have shown the actionv of the pump as being the same on the upstroke as on the downstroke of the pistons thereof, the governing actions on the upstroke andr downstroke are entirely independent. Thus, the pump cylinder may, in actual operation, ll at one end with solid liquid and with a gas-liquid mixture in any proportions at the other end, in which case the valve 6U would govern only when the pump piston is compressing the gas in the gas-liquid mixture. As an example, if the pump cylinder below the pump piston is lled with solidliquid the downstroke will be as shown in the left-hand half of Fig. 21, and if during such downstroke the pump cylinder above the pump piston lls with a mixture of 15% liquid and 85% gas the upstroke will be as shown in the right-hand half of Fig. 22. Similarly, if only one intake or discharge passage were obstructed the valve 60 would govern on the stroke affected but its operation would be normal on the other stroke. Also, if the pump cylinder lls with gas-liquid mixtures at both ends, but in dilerent proportions, the valve 60 would govern on both strokes but during different portions of each, but in all cases controlled by the working load on the pump pis-l ton.

Although I have shown and described a preferred embodiment of the invention, it is to be understood that I do not intend to be limited thereto, but desire to be alforded the full scope of the following claims.

I claim as my invention:

1. In a device of the character described, the combination of: a cylinder having a piston therein; a pair` of sources of iluid respectively providing high and low pressures; a pair of passages connecting said sources to the respective ends of said cylinder for applying said high and low pressures to the respective ends of said piston to move said piston in said cylinder, said piston moving at a normal speed in response to predetermined rates of iiow of fluid through the respective passages; hydraulically actuable valve means controlling one of said passages and movable from a closed position through a partially open, throttling position to a fully open position. said valve means, when in said throttling position, metering uid through said one passage at a restricted rate of flow substantially less than said predetermined` rate of ilow therethrough so as to restrict said piston to a speed substantially less than said normal speed, said valve means being retainable in said throttling position by balancing the pressure forces applied thereto; and control means for balancing the pressure forces applied to said valve means.

2. ln a device of the character described, the combination of a cylinder having a piston therein; a pair 0I' sources of fluid respectively providing high and low pressures; a pair of passages connecting said sources to the respective ends of said cylinder for applying said high and low pressures to the respective ends of said piston to move said piston in said cylinder, said piston moving at a normal speed in response to predetermined rates of flow of fluid through the respective passages; hydraulically actuable valve means controlling one of said passages and movable from a closed position through a partially open, throttling position to a fully open position, said valve means, whenr in said throttling position, metering fluid through said one passage at a restricted rate of ow substantially less than said predetermined rate of flow therethrough so as to restrict said piston to a speed substantially less than said normal speed, said valve means being retainable, in said throttling position by balancing the pressure forces applied thereto; and control means for balancingV the pressure forces applied to said valve means, said control means including port means for applying to an area of said valve means a pressure preventing movement of said valve means beyond said throttling position toward said open position, said port means including a rst port communicating with said one passage and a second port communicating with said area of said valve means, said ports communicating with each other when said valve means is in said throttling position.

' 3. In a device of the character described, the

combination of: a cylinder having a piston there-- in; a pair of sources of iluid respectively providing high and low pressures; a pair of passages connecting said sources to the respective ends of said cylinder for applying said high and low pressures to the respective ends of Asaid piston to move said piston in said cylinder, said piston moving at a normal speed in response to predetermined rates of flow of iiuid through the respective passages; hydraulically actuable valve means controlling one of said passages and movable from a closed position through a partially open, throttling position to a fully open position, said valve means, when in said throttling position, metering iluid through said one passage at a restricted rate of flowA substantially less than said predetermined rate of flow therethrough so as to restrict said piston to a speed substantially less than said normal speed, said valve means being retainable in said throttling position by balancing the pressure forces applied thereto; and control means :operating in response to a reduction in a load on said piston for balancing the pressure forces applied to said valve means, said control means including port means for applying to an area of said valve means a pressure preventing movement of said valve means beyond said throttling position toward said open position, said port means including a rst port communicating with said one passage and a second port communicating with said area of said valve means, said ports communicating with each other when said valve means is in said throttling position.

4. A device as defined in claim 3 wherein said one passage communicates with said source of fluid under low pressure.

5. A device as defined in claim 3 wherein said one passage communicates with said source of fluid under high pressure.

6. In a device of the character described, the combination of a cylinder having a piston therein; a pair of sources of iiuid respectively 'providing high and low pressures; a pair of passages connecting said sources to the respective ends of said cylinder for applying said high and low pressures to the respective ends of said piston to move said piston in said cylinder, said piston moving at a normal speed in response to predetermined rates of flow of fluid through the respective passages; and valve means controlling one of said passages and movable from a closed position through a partially open, throttling position to a fully open position, said valve means, when in said throttling position, metering uid through said one passage at a restricted rate of ow substantially less than said predetermined rate of flow therethrough so as to restrict said piston to a speed substantially less than said normal speed.

7. In a valve device, the combination of: a valve housing having an inlet adapted to be connected to a source of operating uid under relatively high pressure; a valve member in said housing and of the differential area type having a small end adapted to be subjected to said inlet pressure and a large end adapted to be alternately subjected to said inlet pressure to move said valve member from a primary to a secondary position; and iiuid passage means continuously communicating with said inlet `and an area of said valve member for preventing said valve member from stopping on dead center during movement between said positions.

8. In a valve device, the combination of t a valve housing having an inlet adapted to be connected to a source of operating uid under relatively high pressure; a valve member in said housing and of the differential area type having a small end adapted to be subjected to said inlet pressure-and a large end adapted` to be ,alternately subjected to said inlet pressure to move said valve member from a primary to a secondary position; iirst port means adapted to convey operating fluid to said large end to move said valve member a nrst increment of its total movement between said positions; second port means adapted to convey operating iiuid to said large end to move said valve member a second increment of its total movement between said positions; and fluid passage means continuously and restrictedly communicating with said inlet and said large end oi' said valve member for preventing said valve member from Ystopping on dead center during movement between said positions.

9. In a valve device, the combination of: a valve housing having an inlet adapted to be connected to a source of operating uid under relatively high pressure; a valve member in said housing and of the differential area type having a small end adapted to be subjected to said inlet pressure and a large end adapted to be alternately subjected to said inlet pressure to move said valve member from a primary to a secondary position; first port means adapted to communicate between said large end and a point of low pressure discharge so as to permit said high pressure operating fluid to move said valve member through a rst increment of its movement between said positions; second port means adapted to communicate between said large end and a point of low pressure discharge so as to permit said high pressure operating fluid to move said valve member through a second increment of its movement between said positions; and fluid passage means continuously and restrictedly communicating with said inlet and said large end of said valve member for preventing said valve member from stopping on dead center during movement between said positions.

l0. In a valve device for use in a fluid operated pump in a well producing sand in the pumped oil, the combination of: a valve housing; a movable valve member in said housing and of the differential area type having a small end adapted to be subjected to relatively high inlet pressure and a large end adapted to be alternately subjected to said inlet pressure to move said valve member between two operating positions; and passage means adapted to alternately connect said large end to a low pressure discharge port, said passage means being relatively long and tortuous in character so as to inhibit the entrance of sand therethrough into engagement with the central section of said valve member.

1l. In a fluid operated motor device, the combination of a motor cylinder having a motor piston therein; a fluid discharge passage communicating with one end of said motor cylinder, including a discharge passage wall; a source of operating iluid under relatively high pressure; means for supplying said operating iluid to the other end of said cylinder to move said piston therein at a normal rate at a normal working load thereon; a differential-area type valve member having one end larger than the other, said valve member being movable between primary and secondary points and through a throttling position to connect said discharge passage with a relatively low pressure discharge port, and inincluding a valve wall, the large end of said valve member being alternatively exposed to the pressure of said operating uid; throttling means provided in one of said walls and providing restricted fluid communication between said passage and said discharge port when said valve iiiember is in said throttlng position, ythe crosssectional area of said throttling means when said valve member is in said throttling position being sufficiently small that uid cannot exhaust from said one end or" said piston ata rate high en ough to permit said piston to move at -a rate greater than said normal rate; a governing port communicating with said passage; `and passage means adapted ,to provide .fluid communication between said governing port and said large end of said valve member when said valve :member is in said throttling position so as to admit iluid pressure from said .passage to said large end of said valve member so as to maintain said valve member in said throttling position.

l2. Ina uid operated motor device, :the oombination of: a motor cylinder having a motor piston therein; a vuid discharge passage communicating with one end of said motor cylinder, including a discharge passage Wall; a source oi operating uid under relatively high pressure; means for supplying said operating fluid to the other end of said cylinder to move said piston therein at a normal rate at a normal working load thereon; a diierential-area type valve meinber having one end larger than .the other, said valve member being movable between primary and secondary points and through a throttling position to connect said discharge passage with a relatively low pressure .discharge port and including a valve Wall, the largeend of said valve member being alternatively exposed to the pressure of said operating fluid; throttling means provided in one of said walls and providing ren stricted fluid communication between said .pasN sage and said discharge port when said valve member is in said throttling positiornthe crosssectionalarea of said throttling means when said valve member is in said throttling position ybeing sumciently small .that any tendency of said piston to move at a rate higher than said normal rate Will substantially raise the fluid pressure in said passage; a governing portcommunicating with said passage; and passage means radapted to provide iluid communication Vbetween said governing port and said large end of said valve member when said valve member is in said throttling position so as to admit fluid pressure from said passage to saidlarge end oi said valve member so as to maintain said valve member in said throttling position so long as the fluid pressure in saidzpassage remains above a pren determined value.

13. In a valve device for use ina uid operated pump in a well producing said in the pumped oil, the combination of: a kvalve housing having a discharge port adjacent the upper end thereof and a passage in the wall of said housing and extending a substantial distance from said discharge port and communicating therewith; and a tubular Valve member in said housing, having a valve port communicating with the interior of sai-:l valve member, said valve member being movable in said housing to a position in which said valve port communicates :with said passage at a point spaced a substantial distance from said discharge port, thereby inhibiting the entrance of sand into engagement'with .said valve member in the vicinity of said valve port.

14. In a valve device for use in a fluid operated pump in a well producing sand in the pumped oil, the combination of: a valve housing having a discharge port adjacent the upper end thereof and a passage inthe Wall Yof said housing land extending a substantial vdistance from said .dis-

charge port and communicating therewith; .and a tubular valve member in 'said housing, having a valve port communicating with the interior of said valve member and passage means in said interior communicating between said valve port and one end of said valve member, said valve member being movable in said housing vto a position in `which vsaid valve port communicates with said passage at a point spaced a substan tial distance from said discharge port, thereby inhibiting vthe entrance of sand into engagement with said valve member in the vicinity of said valve port.

15. ln a valve device for a iluid operated well pump, the combination of: a valve housing; Ya tubular valve member disposed in said housing and movable relative thereto, said valve member being of the differential-area type having one end of relatively smallcross-sectional area and another end of relatively large cross-sectional area; nrst Valve means normally providing fluid communication with'said large end during a rst portion of the movement of said valve member, said rst portion of ysaid movement including movement through a dead center'position; second valve means for providing uid communication with said large'end during a second part of the movement of said valve member, said second part of said movement completing the travel of said valve member; and restricted passage means providing uid communication with said large end during said movement through said dead center position and until said second'valve means is fully open so that 'if said rst valve means closes during said first portion of said movement when said valve member is in said dead center position. said valve member Will move to one end of its travel.

16. Ina valve device for a uidroperated well pump, the combination of: a valve housing hav'- ing a source of operating uid under relatively high pressure and having a low pressure dis charge port; a valve member in said housing and movable relative thereto, said valve member being of the differential-area type having one end of relatively small cross-sectional area at all times communicating with said source, and having another end of relatively'large crosssectional area adapted to'be alternately hydraulically connected to said source and said discharge port; rst discharge valve means normally pro'- viding fluid communication between said large end of said valve member and said discharge 'port during a rst portion of the 'movement of said Valve member, said rst portion of said movement including movement through a dead center position; second discharge valve means for providing fluid communication between said large end of said valve member and said dis-` charge port during a succeeding portion of the movement of said valve member, said succeeding portion of said movement completing the travel of said valve member; andrestricted passage means providing iiuid communication between said large end andV said sourcewhe'n said valve member is in said dead center positionv and until said second ldischarge valve Ameans is fully open so that if said first Vdischargevalve means closes when said valve member is in said dead center position, the now of fluid from said source through said restricted passage means causes said valve member to reverse its direction 'of movement and complete its movement in such reversed direction.

17.111 a. ,valve device for a fluid operated 25 well pump, the combination of: a valve housing,t having a source of operating uid under relatively high pressure and having a low pressure discharge port; a valve member in said housing and movable relative thereto, said valve member being of the diierential-area type having one end of relatively small cross-sectional area at all times communicating with said source, and having another end of relatively large crosssectional area adapted to be alternately hydraulically connected to said source and said discharge port; rst inlet valve means normally providing fluid communication between said large end of said valve member and said source during a rst portion of the movement of said valve member, said rst portion of said movement including movement through a dead center position; second inlet valve means for providing fluid communication between said large end of said valve member and said source during a succeeding portion of said movement, said succeeding portion of said movement completing the travel of said valve member; and restricted passage means providing fluid communication between said large end and said source when said valve member is in said dead center position and until said second inlet valve means is fully open so that if said rst inlet valve means closes when said valve member is in said dead center position, the flow of fluid from said source through said restricted passage means will cause said valve member to complete its travel.

CLARENCE J. COBERLY.

REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 1,879,262 Hubbard Sept. 27, 1932 2,311,157 Coberly Feb. 16, 1943 

